Hydraulic operating and control mechanism



Jan. 29, 19-46.

C. E. LINDEN ET AL HYDRAULIC OPERATING AND CONTROL MECHANISM 4 Sheets-Sheet '1 Filed 051;. a, 1942 I N V ENTORJ 42x5 Jan. 29, 1946. c. E. LINDEN ETAL HYDRAULIC OPERATING AND CONTROL MECHANISM File d Oct. 13, 1942 4 Sheets-Sheet 2 I A/M /AlW/A liili M F 'VENTOR; BY

' & :1 EIE E E- Jn. 29, 1946. c. E. LINDEN ET AL 2,393,918

HYDRAULIC OPERATING AND CONTROL MECHANI SM Fil e d 00x. 15, 1942 4 Sheets-Sheet s mlm V////////////, I EIEIiIEI IEIIIEIEH- INVENITORS BY W2M$ I rrrru Jan. 29, 1946. c. E. LINDEN ET AL 2,393,913

HYDRAULIC OPERATING AND CONTROL MECHANISM Filed Oct. 13, 1942 4 Sheets-Sheet 4 2 g INVENTOR. Q

Patented Jan. 29, 1946 r HYDRAULIC OPERATING AND CONTROL MECHANISM Carl E. Linden, Norwood, and Raymond H. McClellan, Hamilton, Ohio, assignors to The Fosdick Machine Tool Company, Cincinnati, Ohio, a corporation of Ohio Application October 13, 1942, Serial No. 461,862

4 Claims.

This invention relates to hydraulic systems and is particularly directed to a hydraulic system for controlling and operating the moving parts of a machine. The system herein concerned has utility, for example, in controlling and operating the moving parts of a radial drill. In this and analogous environments, hydraulic motors may be utilized for operating the parts.

This application is a continuation-in-part of Carl E. Linden and Raymond H. McClellan patent application entitled Hydraulic operating and control mechanism, Serial No. 269,188, now abandoned, which was filed April 21, 1939, as a division of a previously filed and co-pending application of the same inventors entitled Hydraulic operating and control mechanism for machine tools, Serial No. 158,070 filed August 9, 1937, and now issued as United States Patent No. 2,319,551.

In the circuit disclosed, a constant supply of fluid is supplied under pressure. The fluid pump is continuously operated. By means of the continuous operation of the pump, a supply of fluid under pressure is maintained for supplying the control circuit of the system. The operation of the parts, such as the motors and levers, requires a much greater pressure than the operation of the valves of the control. However, if the higher pressure is maintained, the pump is constantly working against the full load. This is, of course, inefilcient and places a greater strain on the system. For example, the pressure in the control circuit need be only about 20-25 lbs. per square inch, which is suificient for operating valves, whereas the pressure in the operating circuit should develop about 600 lbs. per square inch.

Accordingly, the present inventors have provided a hydraulic system for controlling and operating the moving parts of a machine in which the fluid pump is constantly driven and wherein the discharge of the pump is bypassed or returned to the supply, thereby relieving the pump of the strain of operating against substantial head pressure. Toward this end, a secondary c'ontrol'circuit is supplied, altered by the manipulation of any of the control'levers ofthe moving parts,

whereby the pump is'caused to deliver fluid into the system under pressure suificient for the operations intended. v

The arrangement accomplishing this end includes a relief valve means arranged so that when the pump is operating and none of the control valves have been moved to operative position" for any of the mechanisms, the fluid 'passes two ways from the valve, namely through a bypass and through thesecondary or control'line. In both instances, it returns to the tank. Thus, the pump is not working against full load unless the mechanism is being operated. The head pressure created is not substantial, since the fluid is moving back into the supply tank under the control circuit pressure of approximately 20-25 lbs. per square inch. 3 c

This general arrangement of the hydraulic system simplifies the same and renders it more efiicient and less wearing on the parts of the system including the pressure fluid means and the conduits.

In a circuitof thisftypeas applied to a radial drill, for example, it is necessary to provide an intercontrol between certain of the control parts which will delay or prevent the operation of one pending the completion of the operation of the other. Specifically, in the operation of the arm of the radial drill, the arm clamp must be released before the arm elevating motor is operated.

Therefore, it has been the object of the present inventors to provide a system wherein means is included normally blocking the flow of fluid under pressure from the valve controlling the operating means, movement of which is to be delayed until the movement of the first operating means has been consummated.

More specifically, it has been a further object to provide a delaying valve between the control valves actuated automatically for delayed flowto the valve of the control part to be moved last. It has been arranged that the delaying valve will not open until the first control part has fully com' pleted its stroke at which time its valve will open the passageway to the delaying valve, permitting it to move .to open position. In other words, the delayin valve is normally held in fully blocked position.

In systems of this type, certain of the devices to be operated do not require and should not be supplied with high pressure fluid, and control of the system for supplying different pressures is important.

Accordingly, it has been a further object of the control means includes passageway arrangements which block passage of fluid through the low pressure unloader valve unless the control valve is moved into its operating position. When thus moved, the vent line is blocked and operating pressure develops. This pressure would develop to 600 lbs. were it not for the fact that the line is then opened through to the low pressure relief valve, bypassing the high pressure relief valve through the control valve.

Other objects and certain advantages will be ous valves eventually returning to the tank. The

arrangement is such that when the pump is opcrating and none of the valves have been moved more fully apparent from a description of the accompanying drawings in which:

Figure 1 is a diagrammatic view illustrating the system showing the various devices in the circuit for operating certain machine elements as, for example, those of a radial drill such as the column clamp, arm clamp, head traverse and arm elevation, the system being shown in'rieutral position and the low and high pressure relief valves being shown.

--Figure '2 is a diagrammatic View illustrating the system but showing thevarlous valves in position'fo'r causing operation of the respective control motors; in other words, releasing the clampsrnoving the arm and traversing the head, and further illustrating the delaying valve in opened position admitting fluid to tharm ole,-

vatingmotor. i

Figure 3 is a diagrammatic view of the system showing the'various control valves reversed from the positions shown in Figure 2 for drawing the head in a reverse direction and changing the direction "of the elevation of the arm. 7

Figure '4 is a diagrammatic view showing the system as previously illustrated in the applicatio and patent referred 'to above.

Figure is a diagrammatic view showing a conventional representation of a drill arm and screw and-nut elevating means, and also showing the motor for driving the elevating means and the clamp actuating apparatus.

. 'Theppump is generally indicated at H) and is system and permitting free circulation when themechanisms are not being used. This bypass or vent line is automatically closed when the fluidis used for o-peration and is reflective for closing off the return conduit to the tank, thereupondirecting the fluid throug'hthe system.

Referring to Figure 1 of the drawings, the pump 10 is diagrammatically shown, As stated, the fluid is drawn to a pump through the conduit- H from the tank H. The conduit ll includes a;check Valve [1 at its lower end, The tank I2 includes a breather opening [8. The relief or bypass valve -l4 is in-connection withthe discharge side of the pump by way of .pipe I-3.- The return ipe or bypass iE-is connected to one end of thevalve; 7 s

The :rietails of the valve 14 are not fully disclosed, a diagrammatic form of illustration being selected to eliminate thedetails of this type of valve, which is well known. A floating valve 19 to'operative position for any of the mechanisms,

the fluid passes two way from the valve, namely,

through the bypass l5 and through the secondary control vent pipe [6, in both instances returning tothe tank. Thus, the pump is not Working against full load, unless the mechanism is being operated, no substantial head pressure being created since the fluid is moving back into the tank under only normal pressure of 20-25 lbs. through the pipe if). The port 22 is small, being approximately one-sixteenth of an inch in diameter. The vent line or conduit leis larger,

being: approximately one-fourth of an inch in diameter. The fluid passing through thel'in'e i6 is under about 20-25'lbs. per square inch. According'ly, when the supply is not-being used, the electric motor is not being loaded unnecessarily and no horsepower 'isbeing taken from the drive to the drill.

The relief valve 'co'ntrol pipe or conduit I'B has been arranged with respect to-the valves so that movement. of any one of the'valves to a motor operating position will block this line and cause thepressure in the chamber at the back of the valve and the pressure within the main valve chamber or in the pipe If: to equalize. Thereupon, the spring 21 acts to move the valve across to the seatlfl. The fluid then must pass into the main supply pipe 23l'eading to the 'variousvalves,

. and the head pressure builds up sufficiently for.

operating any one of the respective motors.

This main supplyline 23 connects to valve 24% which controls, for example, a column 'olamp motor, through a pipe 25'. As shown in Figure 1, the valve 24 is in clamping position. In this position; the fluid passes from the-pipe 25 throughv a-groove 25 of the valve to a pipe 21. This latter pipe connects, to one end of the column el-amp operating -motor=2 8. The piston 290i the column clamp motor is then forced in column-clamping direction. 7

-It-will be understood at this point thatrthe column clamp is-self-sustaining in each position; thatisto say,;it isunnecessar-y to maintain the pressure fluid: on either side-of the piston 29 to hold the clamp in either clam-peel or .unclamped position. Theclamping action has previously o ccu-r'redand the piston is stationary as shown in Figure 1; In 'thi-s-clamping-action, the fluid head is exhausted trom'the' other end of the cylinderthroughapipe i'lil, returningtothe valve and pass-' ing through-groove-M, andgthence by way of exhaust conduit 3-2',to---t-he tank,

Associated with the motor 28 is a valve 33. This; valve-has--its stem connected to -the piston rod -34 ofthe motor 28 by means of a bar 35. This bar is, free to slide upon the; valve; stem be-- tween the shoulders 36 and 3 thereof. When the motor piston is moved to clamping-position, as shown in Figure 1, the valve 33 is shifted in'the last phase of the piston movement tothe position indicated; V j

it-wilrbenotedthat therreliefvalve control vent conduit lGextends to the -valve-24.-1t *has two exits trom the valve, "namely, '38 and- 39; 'one at each side or the conduit: it. These conduits ex tend-to the reversing valv 33 and pass through the bore thereof at spaced points joining together to continue the pipe thereafter. .The valve 24 includes a groove 40 positioned and of a length for connecting the pipe l6 to either conduit 38 or 39.

In th positions shown, the valve 24 has blocked conduit IS in the beginning when the groove 41 of the valve 33 has'been disposed in position for maintaining the conduit 38 in open condition. When the motor piston 29 moves to clamping position, the groove 4| lines up with the sections of the conduit 39. This control conduit is'then uninterrupted, passing through the respectivevalves by way of groove 40 and groove 4 l.

The supply pipe 23 extends to the arm clamping valve 42 by way or two conduits, namely, 43 and. In Figure 1, the arm clamp is shown in clamped position and, due to the interconnection between the arm clamp valve 42 and the arm elevating motor control valve 45, the control valves maintain the elevating motor 46 in stationary condition. In this position, the arm is clamped since the oil passes to the conduit 44 through the groove 41 of valve 42 and then through conduit 48 to the end of the clamping motor cylinder 49. A control valve 50 for the relief valve control line is associated with the motor 49. This valve is fixed to the piston rod of the motor 49 by means of a bar and must move therewith. In the unclamped position of the arm clamp, the groove 5| of this valve is disaligned from the control pipe l6 where it passes across the bore of the valve. In the clamped position, the groove 5| is aligned with the sections of the pipe l6 and there is no interruption to the flow so that the pump simply bypasses through the conduit I I5 back to the tank. This occurs,however, after the clamp has been set.

Due to the fact that the arm clamp is fixed to the elevating mechanism control valve, the valve 42 must have duplicate positions at each side oi clamped positions so that unclamping will occur in either direction. Toward this end, a groove 52 is provided, adjacent groove 41, which will exhaust the end of the motor cylinder 49 in the unclamping operation either through conduit 48 through exhaust conduit 53, or through a branch conduit 54 of conduit 48 through exhaust 'conduit 53.

The arm clamping motor 49 is exhausted in the clamping operation through conduit 55 leading back to the valve 42 through one of the branches 56 by way of groove 51, and thence through either exhaust branch 58 through conduit 53 back to the tank. Duplicate conduits 5656 are provided at either side of the groove 59 which is in connection with the supply conduit 43. It will be seen that when the valve is either shifted tothe right or left, supply conduit 43 is connected to the motor 49 through either of the conduits 56-56 and the. unclamping'movement of the motor ,49 will take place.

Du -to the provision of the valves 33 and 56, the pressure does not drop in the system until the motors 28 and 49 have moved to fully clamped or unclamped positions. This is true even though the levers controlling the main valves '24 and. 42 of these motors-be released to neutral.

The elevating motor control valve 45 receives the fluid supply by way of pipe 60 which-includes an unloader valve 6|.

.The supply line 60 connects to pipe 55 so as to receive the fluid under pressuref r theoperation (see Figure 1, groove 5|).

of the elevating motor as following the arm unclamping movement. Either of thegro'oves 621 of valve 45 connects the pipe 60 with the motor- 46 through pipes 63 or 64 respectively, depending uponthe direction of the movement of the ele vating motordesired, that is to say, dependent 'upon the position of its control lever. In the position shown in Figure 1, the motor 46 is atrest since the valve has closed off passage 60. The grooves 62 also connect conduits 63 and 64 alternately to exhaust conduits 65 and 66. Accordingly, when the valve 45 is shifted, let ussay to the right, the pipe 60 connects to ipe 64 and the motor is then driven. The fluid continues through conduit 63 and conduit 65, through the exhaust line 61 to the tank.

However, unloader valve 6| will not allow the fluid to pas through the motor 46 until the arm clamping motor has been operated and has released the arm, and a delay is provided preventing operation of the elevating motor until the arm clamping motor has functioned.

To provide this result, the valve 50 has another groove 68. A conduit 69 extends from the supply line 23 normally through this groove 68 by way of a conduit 10 to the end of the delay valve 6! oppo site to-the connection of the conduit 60. The valve element H is engaged against a spring 12.- Thus, there is normally a line pressure-exerted against the valve ll preventing it from uncovering the section of conduit 60 leading to the'arm elevating motor control valve. However,- when the valve 50 is moved to arm unclamping posi tion, this line pressure is blocked and the valve 1| opens easily against the spring to operate the arm elevating motor. The spring 12 provides a resistance or cushion. The oil control'conduit l6 passes through valve 45 by way of a groove 13 aligned with the conduit when the valve is in neutral position. This groove is essential since, upon the completion of the arm clamping motor stroke, the control passageway will have been reopened However, the passage of oil through the control passage is still blocked as long as the elevating motor control valve is in either elevating or lowering position.

.The supply pipe 23 is extended to the head traverse control valve 14 which is a duplicate of the elevating motor control valve so that its passageways are numbered in duplicate. The head traverse motor 15 may be operated slowly or rapidly due to the provision of chamfered edges 16 on that portion of the valve which blocks the supply when the valve is in neutral. In other words, by inching the lever, a variable inlet to the valve is effected. This valve 14 includes the same arrangement for controlling the passage of oil through the control pipe [6 so that the valve is efiective for blocking this pipe to supply the necessary pressure fluid to the motor 75 when desired.

Operation of the various motors at the beginning of motor operation, pressureis developed. Thereupon, the fluid moves through pipe 25, pipe 30, and the clamp is unclamped. The exhaust takes place through pipe 21, through groove 26 01 valve 24, and through exhaust pipe 32 tothe tank.

- .When the column clamp has been unclamped;

the: flow ofi oil througlr they control: conduit: M res-established through pipe 38; grooved-I oi valver33g groove:- leof valve 50;. and thence: to! theitankt V v g The next move the operator makes; is te move; the armclamp-and elevating motor cont-rob leverin either direction dependent upon; whether or:

not-the arnr isto'beraised' or lowered (one of these directions is assumed-in. Figure Z and the; other in Figure 3; blocksthe control conduit to; since-thegroove 1:3: is disalig ned; This causes the: pum'mto deliver fluid under pressurev through pipe 43'; groove 58,;

operating pressure is: available; Whemtheoper: .atoro stops the elevating: motor by shifting the controblever to neutral, th'e armclampirig valve"- will be im position for clamping;- the arm: clamp: in the final phase. This is possible" sincefi the"- controlvalve 50 has-still blocked the controlxpipe Hi. The head traverse motor may: thenz-ber op erated for moving the h'ead-valonglthe ai'inz This isdone by shifting" the head traverse controhlever in either directiom. one: direction being shown in'Figure 2-andl the other in=Eigure 3." Asrsiio wn Movement: or the valve 45 ment topressure directing and pressumreleas:

in Figures 2'- and 3, the controlaoonduiti6 is blocked uponthe movement of the valve: and: fluid pressure is: availablepassing through: line: 23; groove 7 62-, conduit 64; the? motor 15%; conduit 63, other groove 62 exhaust; conduit ligand-the main exhaustconduit 61;

By inching the valve through=mampulatioin of= the control lever f or positioning? the chamfei'ed: edges 16 of the: valve: the speed of movement of the hydraulic motor: of" thehead may?" be variedrv V Asexplained-previously, thesyStemdsarrafigedso thatit will normally? unload at about GOO-files; pressure per square inch-,. which: is the r correct pressure for operating most of? the: mechanism; However; v-in this case,-the head".traversemotor 1 5 shouldronlyl have deliveredato itabout 150-165 i per squareinch Thus;- the following arranger menthas-beenprovidedr An unloader conduit 181 extends to amunioauer valve indicatedat T 9" and Y the? line. extends fi'dm this unloaderlvalve to: thetanli'; rinsuniba'der line-extendsfrom the :maiz'rcontrorvmve l1? co'ri necting to it on the same side as the vent-line IS. The vent line L6, as stated, is" connected through the head traverse valve 14 to a groove 131 H second unload'e r line 8o' extendsfromi this vent line" I 6 just' before" it enters"'-t1ie"vaivet 13f line also enters into the"va;lve" 1'4," particularly agroovesl therein. Normally, this. second unloadei'" line is blocked. conduits s21 tap-'into thevalve M at either side of "tile-groove andrex ten'd' througha common conduit 83- to an un loader valve 84 which: unloads at 150-lbs? per squareinch.. Fro-mthis-latter unloader valvevthe line extends to the tank, bypassing; thefafiist named unloader valves Thus; when the valvefor coincidental movemenvto pressure di'rectifig zgsosgere thezhead traverse motor is-movedeither way, thesecond; unloader line is connected and; no more than 150 lbs; per square'inch of: pressure canbe delivered to the head traverse motor- 15. e

The subjectmatter illustrated in Figure l 4 is the same as that previously described exceptthat the unloader valves I9 and- 84; have; been added. Als0-,. the-delay valve 6l-'intlre disolosure of Figure 4- opensas pressure develops in the; arm-unclamping motor following; completion of! the unclam-ping aotion which pressure is suflieient to" move; the; delay valve against its-spring and permittheflow oi -fi-uid to the valve controlling the arm elevating motor In other words, in" this; form the conduit 'l llisomitted Having-described our invention weclaim; 7

1L Ahydraulic system comprising a -fluid mo-; tor for locking and unlocking-,anelement, a'fiuid motor for actuating the element aconduit system including said motors a source of pressure fiuid,.. respective valves tor said locking; and actuatingmotors: coupled; for coincidentall movee inggpositions a control valve ooupled wit h said locking, motor and; pressure: responsive valving means in said conduitsystem normally blocking flow between said respective--locking motor and actuatingmotor valves, butgoverned joy said-con-' trol val ve to permit transference of pressuretcsaid'actuating fluid motor-afterunlo cking-rand hefore-locking of said fi-LlldJOGli-ing motor in response to pressure transferredto-said fluid-locking motor from saidIv source, upon actuation of said valves.-

2'=-.A hydraulic systemPinc-Iuding, apfiuid motorfor locking and unlocking anelement ofthe tooLra fluidmotor effective to actuate said: 616-- ment} a SQUICef-- pressure flu-1d,, akconduitssys tem leading, from saidsourceincluding avalve for said locking motor and a valve for saidtaotu ating. motor, a control valve: operated unison with said lockingmotor during=- at least the-last phase of I movement thereof} and-- valvinga means v normally isolating. said locking motor and actuating', motor valves in said systemg the valving: means Beingresponsive to pressure in-saiddoek ing. fluiduhotor and governed; by said pdntrol valve to permit. pressure transfer; insaid system to; said-actuatingifluiwmotor in-delayed-relation'-= sh'ipromovement o'f'said locking/fluidmotor;

3. A hydraulic system comprising a fiui'd mo tor for lockingland unlocking an element a fluid motor foractuating the element; F a. conduitsys'-- tem including said motors, a-sourceof-= pressure fluid; respective valve's'foi 'said' motors: coupled jog an pressu e reIeaSmgposiuoaS: and vaiv ng; me in said' conduit sv'stein normally" blocking flow between said respective valves, control valve" .t o rbe b u: piee mmmacmemarmovement wpressure ar:

sponsive valve for opening said valve in response to the pressure transferred from the locking motor thereto, whereby said pressure responsive valve permits flow of pressure fluid from said 5 locking motor valve to said actuating motor valve.

CARL E. LINDEN. RAYMOND H. McCLELLAN. 

